CN216347033U - Pipe fin monomer, heat exchanger and air conditioner - Google Patents
Pipe fin monomer, heat exchanger and air conditioner Download PDFInfo
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- CN216347033U CN216347033U CN202122734731.7U CN202122734731U CN216347033U CN 216347033 U CN216347033 U CN 216347033U CN 202122734731 U CN202122734731 U CN 202122734731U CN 216347033 U CN216347033 U CN 216347033U
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Abstract
The utility model discloses a tube fin monomer, a heat exchanger and an air conditioner, wherein the tube fin monomer comprises a body, an inlet hole and an outlet hole which are communicated along the thickness direction of the body are respectively formed at two ends of the body in the length direction, a plurality of refrigerant inlets are formed on the inner surface of the inlet hole, a plurality of refrigerant outlets are formed on the inner surface of the outlet hole, a plurality of heat exchange channels are defined in the body, the plurality of heat exchange channels are arranged at intervals along the width direction of the body, each heat exchange channel extends along the length direction of the body, and both ends of each heat exchange channel in the length direction are respectively communicated with the refrigerant inlet and the refrigerant outlet, the cross sectional areas of at least two of the heat exchange channels are unequal, and the cross-sectional area of the heat exchange channel positioned at the upstream in the at least two heat exchange channels is larger than that of the heat exchange channel positioned at the downstream, and the width direction of the body is parallel to the airflow direction. The tube fin monomer has good heat exchange performance.
Description
Technical Field
The utility model relates to the technical field of air conditioners, in particular to a tube fin single body, a heat exchanger and an air conditioner.
Background
In the related art, in a heat exchanger, a first heat exchange medium (e.g., air, etc.) flows along a set direction to sequentially exchange heat with a second heat exchange medium (e.g., water, or a refrigerant, etc.) in a plurality of heat exchange channels of the heat exchanger; however, in the set direction, the temperature difference between the second heat exchange medium and the first heat exchange medium in the upstream heat exchange channel is large, and the temperature difference between the second heat exchange medium and the first heat exchange medium in the downstream heat exchange channel is small, so that the heat exchange amount of the downstream heat exchange channel is low, and the heat exchange amount of the whole heat exchanger is unevenly distributed.
Moreover, when the second heat exchange medium is a refrigerant, the refrigerant in the upstream heat exchange channel can be rapidly gasified, and the heat exchange amount of the refrigerant in the downstream heat exchange channel is small, so that the refrigerant in the heat exchange channel can flow out in a two-phase state, the gasified refrigerant can not fully exchange heat, the heat exchange amount is reduced, the heat exchange amount of the heat exchanger is obviously reduced, and the heat exchange performance of the heat exchanger is influenced.
SUMMERY OF THE UTILITY MODEL
The present invention is directed to solving at least one of the problems of the prior art. Therefore, the utility model provides a tube fin single body which has good heat exchange performance.
The utility model also provides a heat exchanger with the tube fin monomer.
The utility model also provides an air conditioner with the heat exchanger.
According to the tube fin monomer of the embodiment of the first aspect of the present invention, the tube fin monomer includes a body, an inlet hole and an outlet hole penetrating along a thickness direction of the body are respectively formed at two ends of the body in a length direction, a plurality of refrigerant inlets are formed on an inner surface of the inlet hole, a plurality of refrigerant outlets are formed on an inner surface of the outlet hole, a plurality of heat exchange channels are defined in the body, the plurality of heat exchange channels are arranged at intervals along a width direction of the body, each heat exchange channel extends along the length direction of the body, two ends of each heat exchange channel in the length direction are respectively communicated with the refrigerant inlets and the refrigerant outlets, cross-sectional areas of at least two heat exchange channels of the plurality of heat exchange channels are unequal, and the cross-sectional area of the heat exchange channel located at an upstream side of the at least two heat exchange channels is larger than the cross-sectional area of the heat exchange channel located at a downstream side, the width direction of the body is parallel to the airflow direction.
According to the tube fin monomer provided by the embodiment of the utility model, the cross sectional areas of at least two of the plurality of heat exchange channels are different, and the cross sectional area of the heat exchange channel positioned at the upstream in the at least two heat exchange channels is larger than that of the heat exchange channel positioned at the downstream, so that the gasification of a refrigerant in the upstream heat exchange channel can be inhibited, and the flow of the refrigerant in the downstream heat exchange channel can be inhibited, so that the enthalpy change difference of the plurality of heat exchange channels of the tube fin monomer from a refrigerant inlet to a refrigerant outlet is reduced, the enthalpy change from the refrigerant inlet to the refrigerant outlet of the plurality of heat exchange channels is ensured to be more uniform, and the heat exchange performance of the tube fin monomer is improved.
In some embodiments, the cross-sectional area of a plurality of the heat exchange channels decreases sequentially in the direction of the gas flow.
In some embodiments, the number of the heat exchange channels is N, in the airflow direction, the cross-sectional area of the first N heat exchange channels is larger than that of the rest heat exchange channels, N, N is a positive integer, N is greater than or equal to 1 and less than N, and the cross-sectional areas of the first N heat exchange channels are equal; and/or the cross-sectional areas of the rest of the heat exchange channels are equal.
In some embodiments, the body is formed as a plate-like structure, and a part of the outer peripheral wall of the heat exchange channel protrudes from the outer surface of the body.
In some embodiments, the plurality of heat exchange channels includes a first heat exchange channel and a second heat exchange channel, and the central axes of the first heat exchange channel and the second heat exchange channel are both located on the thickness central plane of the body; or the central axis of the first heat exchange channel faces one side of the thickness direction of the body and deviates from the thickness central plane of the body, the central axis of the second heat exchange channel faces the other side of the thickness direction of the body and deviates from the thickness central plane of the body, and the first heat exchange channel and the second heat exchange channel are alternately arranged one by one along the width direction.
In some embodiments, the body includes a first plate body and a second plate body, each formed as a plate-like structure, the first plate body and the second plate body being disposed opposite to each other to collectively define the heat exchange channels.
In some embodiments, the first plate body is formed with a first groove, and/or the second plate body is formed with a second groove, and each of the heat exchange channels is formed by the first groove and/or the second groove.
In some embodiments, the first plate body is formed with a first groove, the first groove has a first notch, the second plate body is formed with a second groove, the second groove has a second notch, the first groove and the second groove together define the heat exchange channel, and in the width direction, the first notch and the second notch are arranged just opposite to each other or arranged in a staggered manner.
A heat exchanger according to an embodiment of the second aspect of the utility model comprises: the plurality of tube fin units are arranged at intervals in sequence along the thickness direction of the tube fin units, so that the inlet holes of the bodies are spliced to form inlet channels, and the outlet holes of the bodies are spliced to form outlet channels.
According to the heat exchanger provided by the embodiment of the utility model, the heat exchange performance of the heat exchanger can be improved by adopting the tube fin monomer.
In some embodiments, at least one of the inlet channel and/or the outlet channel is a plurality, a plurality of the inlet channels are arranged in series or in parallel, and a plurality of the outlet channels are arranged in series or in parallel.
An air conditioner according to an embodiment of the third aspect of the present invention includes the heat exchanger according to the embodiment of the second aspect of the present invention described above.
According to the air conditioner provided by the embodiment of the utility model, the cooling or heating performance of the air conditioner can be improved by adopting the heat exchanger.
Additional aspects and advantages of the utility model will be set forth in part in the description which follows and, in part, will be obvious from the description, or may be learned by practice of the utility model.
Drawings
The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:
FIG. 1 is a schematic illustration of a fin unit according to a first embodiment of the present invention;
FIG. 2 is a cross-sectional view of the tube fin unitary body shown in FIG. 1;
FIG. 3 is an enlarged view of portion A circled in FIG. 2;
FIG. 4 is a schematic illustration of a tube fin unit according to a second embodiment of the present invention;
FIG. 5 is a cross-sectional view of the tube fin unitary body shown in FIG. 4;
FIG. 6 is an enlarged view of portion B circled in FIG. 5;
FIG. 7 is a schematic illustration of a fin unit according to example III of the present invention;
FIG. 8 is a schematic illustration of a fin unit according to example four of the present invention;
FIG. 9 is a schematic illustration of a fin unit according to example five of the present invention;
FIG. 10 is a schematic illustration of a fin unit according to example six of the present invention;
FIG. 11 is a schematic illustration of a tube fin unit according to example seven of the present invention;
FIG. 12 is a schematic illustration of a tube fin unit according to example eight of the present invention;
FIG. 13 is a schematic view of a heat exchanger according to one embodiment of the present invention;
FIG. 14 is a schematic view of a heat exchanger according to another embodiment of the present invention, wherein the arrows indicate the direction of airflow.
Reference numerals:
a heat exchanger 200,
A tube fin unit 100, an inlet channel 100a, an outlet channel 100b,
A body 1, an inlet hole 1a, an outlet hole 1b, a heat exchange channel 10, a refrigerant inlet R1, a refrigerant outlet R2,
A first heat exchange channel 10a, a second heat exchange channel 10b,
A first plate body 11, a first groove 11a, a first notch 11b,
A second plate body 12, a second groove 12a and a second notch 12 b.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.
The following disclosure provides many different embodiments, or examples, for implementing different features of the utility model. To simplify the disclosure of the present invention, the components and arrangements of specific examples are described below. Of course, they are merely examples and are not intended to limit the present invention. Furthermore, the present invention may repeat reference numerals and/or letters in the various examples. This repetition is for the purpose of simplicity and clarity and does not in itself dictate a relationship between the various embodiments and/or configurations discussed. In addition, the present invention provides examples of various specific processes and materials, but one of ordinary skill in the art may recognize the applicability of other processes and/or the use of other materials.
Next, referring to the drawings, a fin unit 100 according to an embodiment of the present invention is described.
As shown in fig. 1-3, the fin unit 100 includes a body 1, where two ends of the body 1 in a length direction are respectively formed with an inlet hole 1a and an outlet hole 1b, the inlet hole 1a may be located at one end of the body 1 in the length direction, the outlet hole 1b may be located at the other end of the body 1 in the length direction, both the inlet hole 1a and the outlet hole 1b penetrate through the body 1 in a thickness direction of the body 1, an inner surface of the inlet hole 1a is formed with a plurality of refrigerant inlets R1, and an inner surface of the outlet hole 1b is formed with a plurality of refrigerant outlets R2; a plurality of heat exchange channels 10 are defined in the body 1, the plurality of heat exchange channels 10 are arranged at intervals along the width direction of the body 1, each heat exchange channel 10 extends along the length direction of the body 1, and two ends of each heat exchange channel 10 in the length direction of the body 1 are respectively communicated with the refrigerant inlet R1 and the refrigerant outlet R2, one end of each heat exchange channel 10 in the length direction of the body 1 is communicated with the inlet hole 1a through the refrigerant inlet R1, the other end of each heat exchange channel 10 in the length direction of the body 1 is communicated with the outlet hole 1b through the refrigerant outlet R2, a refrigerant flowing to the inlet hole 1a can flow into the heat exchange channels 10 from the refrigerant inlet R1 to exchange heat, and flows to the outlet hole 1b through the refrigerant outlet R2.
As shown in fig. 1 to 3, at least two heat exchange channels 10 of the plurality of heat exchange channels 10 have different cross-sectional areas, that is, the cross-sectional areas of the plurality of heat exchange channels 10 are not completely equal, or the cross-sectional area of at least one of the plurality of heat exchange channels 10 is different from the cross-sectional areas of the remaining heat exchange channels 10; moreover, the cross-sectional area of the heat exchange channel 10 positioned at the upstream of the air flow is larger than that of the heat exchange channel 10 positioned at the downstream of the air flow in the at least two heat exchange channels 10, the width direction of the body 1 is parallel to the air flow direction, for the at least two heat exchange channels 10, the gas flow exchanges heat with the heat exchange channel 10 with larger cross-sectional area and then exchanges heat with the heat exchange channel 10 with smaller cross-sectional area in the flowing process, in the gas flow direction, the cross sectional area of the heat exchange channel 10 located upstream in the adjacent two heat exchange channels 10 is larger than or equal to the cross sectional area of the heat exchange channel 10 located downstream, that is, for any adjacent two heat exchange channels 10 of the plurality of heat exchange channels 10, the cross-sectional area of the heat exchange channel 10 located upstream of the gas flow is either greater than the cross-sectional area of the heat exchange channel 10 located downstream of the gas flow or equal to the cross-sectional area of the heat exchange channel 10 located downstream of the gas flow.
Note that, the direction of the air flow is parallel to the width direction of the main body 1, and may include: the direction of the air flow is absolutely parallel to the width direction of the body 1, and a small included angle exists between the direction of the air flow and the width direction of the body 1, and the direction of the air flow is approximately parallel to the width direction of the body 1.
Therefore, at least two adjacent heat exchange channels 10 in the plurality of heat exchange channels 10 have different cross-sectional areas, and in the airflow direction, the heat exchange channel 10 with the larger cross-sectional area is inevitably located at the upstream side of the heat exchange channel 10 with the smaller cross-sectional area in the two adjacent heat exchange channels 10 with different cross-sectional areas, that is, in the process of heat exchange of the airflow with the tube fin unit 100, for the two adjacent heat exchange channels 10 with different cross-sectional areas, the airflow exchanges heat with the heat exchange channel 10 with the larger cross-sectional area first and then exchanges heat with the heat exchange channel 10 with the smaller cross-sectional area, that is, in the airflow direction, the refrigerant circulation amount of the upstream heat exchange channel 10 is greater than that of the downstream heat exchange channel 10, so that the gasification of the refrigerant in the upstream heat exchange channel 10 can be inhibited, meanwhile, the refrigerant flow in the downstream heat exchange channel 10 is inhibited, and the enthalpy change difference of the refrigerant from the inlet R1 to the refrigerant outlet R2 of the plurality of heat exchange channels 10 of the tube fin unit 100 is reduced, the enthalpy change from the refrigerant inlet R1 to the refrigerant outlet R2 of the heat exchange channels 10 is more uniform, and the heat exchange performance of the tube fin monomer 100 is maximized.
It should be noted that, for two heat exchange channels 10 with different cross-sectional areas, the hydraulic diameter of the heat exchange channel 10 with a larger cross-sectional area is correspondingly larger, and the hydraulic diameter of the heat exchange channel 10 with a smaller cross-sectional area is correspondingly smaller.
In addition, in the two adjacent heat exchange channels 10 with different cross-sectional areas, in the airflow direction, because the cross-sectional area of the downstream heat exchange channel 10 is smaller, the hydraulic diameter of the downstream heat exchange channel 10 is smaller, so that the flow loss of the air side caused by the downstream heat exchange channel 10 can be reduced, and the airflow flow resistance can be reduced.
According to the tube fin unit 100 provided by the embodiment of the utility model, by arranging at least two of the plurality of heat exchange channels 10 with different cross sectional areas, and the cross sectional area of the heat exchange channel 10 positioned at the upstream in the at least two heat exchange channels 10 is larger than the cross sectional area of the heat exchange channel 10 positioned at the downstream, the gasification of the refrigerant in the upstream heat exchange channel 10 can be inhibited, and the flow rate of the refrigerant in the downstream heat exchange channel 10 can be inhibited, so that the enthalpy change difference of the plurality of heat exchange channels 10 of the tube fin unit 100 from the refrigerant inlet R1 to the refrigerant outlet R2 is reduced, the enthalpy change from the refrigerant inlet R1 to the refrigerant outlet R2 of the plurality of heat exchange channels 10 is ensured to be more uniform, and the heat exchange performance of the tube fin unit 100 is improved.
For example, as shown in fig. 1, the thickness direction of the body 1 is perpendicular to the longitudinal direction of the body 1 and the width direction of the body 1, respectively, and the longitudinal direction of the body 1 is perpendicular to the width direction of the body 1. It is understood that, when the tube fin unit 100 is used in the heat exchanger 200, the placement direction of the tube fin unit 100 may be set according to actual requirements, and is not limited to placing the tube fin unit 100 in the thickness direction corresponding to the up-down direction, but may also place the tube fin unit 100 in the thickness direction corresponding to the left-right direction, the front-back direction, and the like.
In some embodiments of the present invention, as shown in fig. 2 and fig. 3, the cross-sectional areas of the plurality of heat exchange channels 10 are sequentially decreased along the airflow direction, and at this time, the cross-sectional areas of the plurality of heat exchange channels 10 are different from each other, which is beneficial to further ensure that the enthalpy change from the refrigerant inlet R1 to the refrigerant outlet R2 of the plurality of heat exchange channels 10 is more uniform, so as to further improve the heat exchange performance of the tube fin unit 100.
In the following, four heat exchange channels 10 are taken as an example for explanation, and after reading the following technical solutions, those skilled in the art can easily understand that the heat exchange channels 10 are two, three, five, and more than five technical solutions. In the example of fig. 1-3, four heat exchange channels 10 are a first heat exchange channel 10, a second heat exchange channel 10, a third heat exchange channel 10 and a fourth heat exchange channel 10, the first heat exchange channel 10, the second heat exchange channel 10, the third heat exchange channel 10 and the fourth heat exchange channel 10 are sequentially arranged along a first direction, the second heat exchange channel 10 is disposed between the first heat exchange channel 10 and the third heat exchange channel 10, the third heat exchange channel 10 is disposed between the second heat exchange channel 10 and the fourth heat exchange channel 10, and the first heat exchange channel 10 is located upstream of the second heat exchange channel 10 in the airflow direction, so that when the tube fin unit 100 exchanges heat with the airflow, the airflow sequentially exchanges heat with the first heat exchange channel 10, the second heat exchange channel 10, the third heat exchange channel 10 and the fourth heat exchange channel 10, that is the airflow first exchanges heat with the first heat exchange channel 10, Then exchanges heat with the second heat exchange channel 10, then exchanges heat with the third heat exchange channel 10, and finally exchanges heat with the fourth heat exchange channel 10; wherein the cross sectional area of the first heat exchange channel 10 > the cross sectional area of the second heat exchange channel 10 > the cross sectional area of the third heat exchange channel 10 > the cross sectional area of the fourth heat exchange channel 10.
Of course, the present application is not so limited; for example, the cross-sectional area of the first heat exchange channel 10 is larger than that of the second heat exchange channel 10 and larger than that of the third heat exchange channel 10 and larger than that of the fourth heat exchange channel 10; alternatively, the cross-sectional area of the first heat exchange channel 10 is larger than that of the second heat exchange channel 10, that is, the cross-sectional area of the third heat exchange channel 10 is larger than that of the fourth heat exchange channel 10; alternatively, the cross-sectional area of the first heat exchange channel 10 > the cross-sectional area of the second heat exchange channel 10 > the cross-sectional area of the third heat exchange channel 10, which is the cross-sectional area of the fourth heat exchange channel 10.
In some embodiments of the present invention, as shown in fig. 4-6, the number of heat exchange channels 10 is N, the cross-sectional area of the first N heat exchange channels 10 is larger than that of the remaining heat exchange channels 10 in the gas flow direction, N, N is a positive integer, and N is greater than or equal to 1 and less than N. Wherein, the cross-sectional areas of the first N heat exchange channels 10 are equal, and/or the cross-sectional areas of the other heat exchange channels 10 are equal, the method includes the following schemes: 1. the cross-sectional areas of the first N heat exchange channels 10 are equal, and the cross-sectional areas of at least two of the remaining heat exchange channels 10 are different; 2. at least two of the first N heat exchange channels 10 have different cross-sectional areas, and the remaining heat exchange channels 10 have the same cross-sectional area; 3. the cross-sectional areas of the first N heat exchange channels 10 are equal, and the cross-sectional areas of the remaining heat exchange channels 10 are equal.
It should be noted that in the description of the present application, "and/or" is meant to include three parallel schemes, and taking "a and/or B" as an example, the scheme includes a scheme, or B scheme, or a scheme satisfied by both a and B.
In the following, four heat exchange channels 10, that is, n is 4, are taken as an example for explanation, and after reading the following technical solutions, those skilled in the art can easily understand that the heat exchange channels 10 are two, three, five, and more than five technical solutions.
In the examples of fig. 4-6, the four heat exchange channels 10 are respectively a first heat exchange channel 10, a second heat exchange channel 10, a third heat exchange channel 10 and a fourth heat exchange channel 10, the first heat exchange channel 10, the second heat exchange channel 10, the third heat exchange channel 10 and the fourth heat exchange channel 10 are sequentially arranged along a first direction, the second heat exchange channel 10 is disposed between the first heat exchange channel 10 and the third heat exchange channel 10, the third heat exchange channel 10 is disposed between the second heat exchange channel 10 and the fourth heat exchange channel 10, and the first heat exchange channel 10 is located upstream of the second heat exchange channel 10 in the airflow direction, so that when the tube fin unit 100 exchanges heat with the airflow, the airflow sequentially exchanges heat with the first heat exchange channel 10, the second heat exchange channel 10, the third heat exchange channel 10 and the fourth heat exchange channel 10, that is the airflow first exchanged heat with the first heat exchange channel 10, Then exchanges heat with the second heat exchange channel 10, then exchanges heat with the third heat exchange channel 10, and finally exchanges heat with the fourth heat exchange channel 10.
When N is 1, the above scheme 1 may be: the cross-sectional area of the first heat exchange channel 10 > the cross-sectional area of the second heat exchange channel 10 > the cross-sectional area of the fourth heat exchange channel 10, or the cross-sectional area of the first heat exchange channel 10 > the cross-sectional area of the second heat exchange channel 10 > the cross-sectional area of the third heat exchange channel 10 > the cross-sectional area of the fourth heat exchange channel 10; the above scheme 2 and scheme 3 may be: the cross-sectional area of the first heat exchange channel 10 is larger than the cross-sectional area of the second heat exchange channel 10, i.e. the cross-sectional area of the third heat exchange channel 10, i.e. the cross-sectional area of the fourth heat exchange channel 10 (as shown in fig. 4-6).
When N is 2, the above scheme 1 may be: the cross-sectional area of the first heat exchange channel 10 is larger than that of the second heat exchange channel 10 and larger than that of the third heat exchange channel 10 and larger than that of the fourth heat exchange channel 10; the scheme 2 can be as follows: the cross-sectional area of the first heat exchange channel 10 is larger than that of the second heat exchange channel 10 and larger than that of the third heat exchange channel 10, namely, the cross-sectional area of the fourth heat exchange channel 10; the above scheme 3 may be: the cross-sectional area of the first heat exchange channel 10 is larger than that of the second heat exchange channel 10 and that of the third heat exchange channel 10 is larger than that of the fourth heat exchange channel 10.
When N is 3, the above schemes 1 and 3 may be: the cross-sectional area of the first heat exchange channel 10 is equal to that of the second heat exchange channel 10, and is greater than that of the fourth heat exchange channel 10; the scheme 2 can be as follows: the cross-sectional area of the first heat exchange channel 10 > the cross-sectional area of the second heat exchange channel 10 > the cross-sectional area of the fourth heat exchange channel 10, or the cross-sectional area of the first heat exchange channel 10 > the cross-sectional area of the second heat exchange channel 10 > the cross-sectional area of the third heat exchange channel 10 > the cross-sectional area of the fourth heat exchange channel 10, or the cross-sectional area of the first heat exchange channel 10 > the cross-sectional area of the third heat exchange channel 10 > the cross-sectional area of the fourth heat exchange channel 10.
In some alternative embodiments of the present invention, as shown in fig. 3 and 6, the cross-sectional profile of the heat exchange channel 10 is circular, which facilitates the simplification of the structure of the heat exchange channel 10 and the processing; at this time, the cross-sectional area of at least two of the plurality of heat exchange channels 10 is not equal, and it can be understood that the diameter of at least two of the plurality of heat exchange channels 10 is not equal.
Of course, the cross-sectional profile of the heat exchange channel 10 may also be polygonal, elliptical or other special shapes, and the like, only the refrigerant is required to flow in the heat exchange channel 10.
It will be appreciated that the cross-sectional profile shapes of the plurality of heat exchange channels 10 may be the same or different.
In some embodiments of the present invention, as shown in fig. 1 and 4, the body 1 is formed in a plate-shaped structure, so that the body 1 is simple in structure and convenient to process, and meanwhile, the thickness of the body 1 is relatively thin, which is convenient to ensure good heat exchange performance of the body 1. Wherein, partial periphery wall of heat transfer passageway 10 bulges the surface of body 1, then above-mentioned partial periphery wall of heat transfer passageway 10 also can carry out the heat transfer with the air current, is favorable to increasing the heat transfer area of tube fin monomer 100, promotes the heat transfer performance of tube fin monomer 100.
It is understood that part of the peripheral wall of the plurality of heat exchange channels 10 may protrude from the outer surface of the body 1 toward the same side of the body 1, and may protrude from the outer surface of the body 1 toward the opposite side of the body 1.
In some embodiments of the present invention, as shown in fig. 3 and 6, the plurality of heat exchange channels 10 includes a first heat exchange channel 10 and a second heat exchange channel 10, and central axes of the first heat exchange channel 10 and the second heat exchange channel 10 are located on a thickness central plane of the body 1, in this case, if a thickness direction of the body 1 is an up-down direction, an upper side peripheral wall and/or a lower side peripheral wall of the first heat exchange channel 10 may protrude a corresponding surface of the body 1, and an upper side peripheral wall and/or a lower side peripheral wall of the second heat exchange channel 10 may protrude a corresponding surface of the body 1.
For example, in the example of fig. 3 and 6, the upper peripheral wall of the first heat exchange channel 10 and the upper peripheral wall of the second heat exchange channel 10 both protrude from the upper surface of the body 1, so as to enable the upper peripheral wall of the first heat exchange channel 10 and the upper peripheral wall of the second heat exchange channel 10 to both contact with the air flow for heat exchange, the lower peripheral wall of the first heat exchange channel 10 and the lower peripheral wall of the second heat exchange channel 10 both protrude from the lower surface of the body 1, so as to enable the lower peripheral wall of the first heat exchange channel 10 and the lower peripheral wall of the second heat exchange channel 10 to both contact with the air flow for heat exchange, so as to enable the upper and lower sides of the body 1 to have relatively balanced heat exchange performance, and facilitate improving the heat exchange performance of the tube fin unit 100.
Of course, the present application is not so limited; in other embodiments, as shown in fig. 9, the central axis of the first heat exchange channel 10 deviates from the thickness central plane of the body 1 toward one side of the thickness direction of the body 1, and the central axis of the second heat exchange channel 10 deviates from the thickness central plane of the body 1 toward the other side of the thickness direction of the body 1, so that part of the peripheral walls of the first heat exchange channel 10 and part of the peripheral walls of the second heat exchange channel 10 are respectively protruded toward two opposite sides of the body 1, and it is also convenient for the two opposite sides of the body 1 to have relatively balanced heat exchange performance, which is beneficial to improving the heat exchange effect of the tube fin unit 100.
The first heat exchange channels 10 and the second heat exchange channels 10 are alternately arranged one by one along the width direction of the body 1, so that one second heat exchange channel 10 is arranged between every two adjacent first heat exchange channels 10, and one first heat exchange channel 10 is arranged between every two adjacent second heat exchange channels 10. At this time, the upper and/or lower peripheral walls of the first heat exchange channel 10 may protrude from the corresponding surfaces of the body 1, and the upper and/or lower peripheral walls of the second heat exchange channel 10 may protrude from the corresponding surfaces of the body 1; for example, in the example of fig. 9, only the lower peripheral wall of the first heat exchange channel 10 projects from the lower surface of the body 1, and only the upper peripheral wall of the second heat exchange channel 10 projects from the upper surface of the body 1.
In some embodiments of the present invention, as shown in fig. 3 and 6, the body 1 includes a first plate body 11 and a second plate body 12, the first plate body 11 and the second plate body 12 are both formed in a plate-shaped structure, and the first plate body 11 and the second plate body 12 are oppositely disposed to define the heat exchange channel 10 together, so that the body 1 has a simple structure, and facilitates the processing of the heat exchange channel 10.
Optionally, the first plate body 11 and the second plate body 12 are welded; of course, the connection manner of the first board body 11 and the second board body 12 is not limited thereto.
For example, in the example of fig. 3 and 6, the body 1 includes a first plate body 11 and a second plate body 12, the first plate body 11 and the second plate body 12 are each formed in a plate-like structure, the first plate body 11 and the second plate body 12 are disposed oppositely in the thickness direction of the body 1 to define a plurality of heat exchange channels 10 together, and the central axis of each heat exchange channel 10 is located on the thickness center plane of the body 1.
For another example, in the example of fig. 9, the body 1 includes a first plate body 11 and a second plate body 12, the first plate body 11 and the second plate body 12 are each formed in a plate-like structure, the first plate body 11 and the second plate body 12 are oppositely disposed in the thickness direction of the body 1 to define a plurality of heat exchange channels 10 together, the plurality of heat exchange channels 10 include a first heat exchange channel 10 and a second heat exchange channel 10, the central axis of the first heat exchange channel 10 is offset from the thickness center plane of the body 1 toward the thickness side of the body 1, so that part of the outer circumferential wall of the first heat exchange channel 10 protrudes from the outer surface of the body 1 toward the above thickness side of the body 1, the central axis of the second heat exchange channel 10 deviates from the thickness central plane of the body 1 toward the other thickness side of the body 1, so that part of the outer peripheral wall of the second heat exchange channel 10 protrudes from the outer surface of the body 1 toward the other side of the above thickness of the body 1; wherein the first heat exchange channels 10 and the second heat exchange channels 10 are alternately arranged one by one along the first direction. Therefore, when the first plate body 11 and the second plate body 12 are welded and connected, the situation that the heat exchange channel 10 is easily blocked due to welding of the first plate body 11 and the second plate body 12 can be avoided, and the circulation smoothness of the heat exchange channel 10 is ensured.
Of course, the present application is not so limited; in other embodiments, the fin unit 100 is a single piece, for example, the body 1 includes a third plate body formed as a plate-like structure and a heat exchange tube provided on the third plate body and defining the heat exchange channel 10 in the heat exchanger 200, and the heat exchange tube and the third plate body are integrally formed pieces.
In some embodiments of the present invention, as shown in fig. 9-12, the first plate body 11 is formed with a first groove 11a, and/or the second plate body 12 is formed with a second groove 12a, and each heat exchange channel 10 is formed by the first groove 11a and/or the second groove 12a, and the following solutions are included: 1. the first plate body 11 is formed with a first groove 11a, the second plate body 12 is not formed with a second groove 12a (as shown in fig. 10), each heat exchange channel 10 is formed by the first groove 11a, and at this time, the second plate body 12 can cover the first notch 11b of the first groove 11a to form the heat exchange channel 10; 2. the first plate body 11 is not formed with a first groove 11a, the second plate body 12 is formed with a second groove 12a (as shown in fig. 11), and each heat exchange channel 10 is formed by the second groove 12a, at this time, the first plate body 11 can cover the second notch 12b of the second groove 12a to form the heat exchange channel 10; 3. the first plate body 11 is provided with a first groove 11a, the second plate body 12 is provided with a second groove 12a, a part of the heat exchange channels 10 are formed by the participation of the first groove 11a, and a part of the heat exchange channels 10 are formed by the participation of the second groove 12 a; 4. the first plate body 11 is provided with a first groove 11a, the second plate body 12 is provided with a second groove 12a, a part of the heat exchange channels 10 are formed by the participation of the first groove 11a, and a part of the heat exchange channels 10 are formed by the participation of the first groove 11a and the second groove 12 a; 5. the first plate body 11 is formed with a first groove 11a, the second plate body 12 is formed with a second groove 12a, a part of the heat exchange channels 10 is formed by participation of the second groove 12a, and a part of the heat exchange channels 10 is formed by participation of the first groove 11a and the second groove 12a together (as shown in fig. 12); 6. the first plate body 11 is formed with a first groove 11a, the second plate body 12 is formed with a second groove 12a, a part of the heat exchange channels 10 is formed by the participation of the first groove 11a, a part of the heat exchange channels 10 is formed by the participation of the second groove 12a, and a part of the heat exchange channels 10 is formed by the participation of the first groove 11a and the second groove 12 a.
Therefore, the heat exchange channels 10 are flexibly arranged, and the structural diversified design of the tube fin units 100 is convenient to realize.
It is understood that the plurality of heat exchange channels 10 of the fin-and-tube unit 100 may be formed in the same or different manners.
In some embodiments of the present invention, as shown in fig. 3 and 6, the first plate body 11 is formed with a first groove 11a, the first groove 11a has a first notch 11b, the second plate body 12 is formed with a second groove 12a, the second groove 12a has a second notch 12b, the first groove 11a and the second groove 12a together define the heat exchange channel 10, and the first notch 11b and the second notch 12b are oppositely arranged in the first direction, so that the center of the first notch 11b can coincide with the center of the second notch 12b, which is convenient for ensuring the regularity of the cross-sectional profile of the heat exchange channel 10.
Of course, the present application is not so limited; in other embodiments, as shown in fig. 12, the first notch 11b and the second notch 12b are arranged in a staggered manner in the width direction of the body 1, and the center of the first notch 11b and the center of the second notch 12b are arranged at an interval in the first direction, so that the diversified design of the cross-sectional profile of the heat exchange channel 10 is facilitated.
Alternatively, the width of the first notch 11b is equal to or different from the width of the second notch 12b in the first direction. For example, in the example of fig. 3 and 6, the width of the first notch 11b is equal to the width of the second notch 12b, and the first notch 11b and the second notch 12b are oppositely arranged in the first direction, so that both side edges of the first notch 11b and both side edges of the second notch 12b are respectively arranged correspondingly in the first direction to close the heat exchange channel 10. For another example, in the example of fig. 12, the width of the first notch 11b is equal to the width of the second notch 12b, and in the first direction, the first notch 11b and the second notch 12b are arranged in a staggered manner, so that the first plate body 11 and the first groove 11a cover the second notch 12b together, and the second plate body 12 and the second groove 12a cover the first notch 11b together.
For the tube fin unit 100 shown in fig. 3-6, the refrigerant circulation volume of the plurality of heat exchange channels 10 decreases in sequence along the airflow direction, and the heat exchange volume Q of each heat exchange channel 10 can be obtained from the following formula including the area and the inner diameter of the heat exchange channel 10, and from the heat transfer analysis simulation, etc.:
Q＝K·A0·ΔT
ho＝(Ap+η·Af)/Ao×ha
in addition, the optimal hydraulic diameter of the heat exchange channel 10 can be calculated from the designed angle by combining the flow loss calculation formula of the refrigerant in the heat exchange channel 10, and the flow loss calculation formula of the refrigerant in the heat exchange channel 10 is as follows:
wherein Q is the heat exchange amount, K is the total heat transfer coefficient, AoIs the air side heat transfer area, Δ T is the temperature difference, hoFor heat transfer to the air sideRate, ApFor the heat transfer area of the heat exchange channel 10, ApiIs the heat transfer area of the refrigerant side hwIs the refrigerant side heat transfer rate, haThe heat transfer rate of the air side of the body 1 is shown, η is the efficiency of the body 1, Af is the heat transfer area of the body 1, Δ P is the friction pressure loss, λ is the friction coefficient, l is the length of the heat exchange channel 10 (i.e., the length of the flow path), d is the hydraulic diameter of the heat exchange channel 10 (i.e., the hydraulic diameter of the flow path), ρ is the density, and u is the flow velocity.
Optionally, the flow rate of the refrigerant in the heat exchange channel 10 is directly proportional to the heat exchange amount of the heat exchange channel 10, so as to effectively exert the heat exchange performance of the tube fin unit 100.
The heat exchanger 200 according to the embodiment of the second aspect of the present invention includes a plurality of fin units 100, the plurality of fin units 100 are sequentially arranged at intervals along the thickness direction of the fin units 100, so that the inlet holes 1a of the plurality of bodies 1 are spliced to form the inlet channel 100a, and the outlet holes 1b of the plurality of bodies 1 are spliced to form the outlet channel 100b, then the inlet channel 100a is respectively communicated with each heat exchange channel 10, the outlet channel 100b is respectively communicated with each heat exchange channel 10, and the heat exchanger 200 may be formed as a laminated heat exchanger. Wherein the fin unit 100 is the fin unit 100 according to the above-described first aspect of the present invention.
It is understood that, in the heat exchanger 200, when in use, the gas flow can flow through the two sides of the thickness of the fin unit 100, so that the two side surfaces of the thickness of each fin unit 100 are respectively contacted with the gas flow for heat exchange. The thickness direction of the fin unit 100 is the thickness direction of the body 1.
According to the heat exchanger 200 of the embodiment of the utility model, the heat exchange performance of the heat exchanger 200 can be improved by adopting the tube fin unit 100.
Alternatively, the plurality of heat exchange channels 10 of the fin unit 100 may be arranged in parallel through the inlet channel 100a and the outlet channel 100b, that is, the refrigerant is distributed into the plurality of heat exchange channels 10 of the fin unit 100 through the inlet channel 100a, and the refrigerant in the plurality of heat exchange channels 10 flows to the outlet channel 100 b.
In some embodiments of the present invention, at least one of the inlet channel 100a and the outlet channel 100b is plural, for example, the inlet channel 100a is plural and the outlet channel 100b is one, or the inlet channel 100a is one and the outlet channel 100b is plural, or the inlet channel 100a is plural and the outlet channel 100b is plural.
Wherein, when the inlet channel 100a is plural, the plural inlet channels 100a are arranged in series or in parallel; if the plurality of inlet passages 100a are provided in series, the refrigerant flows through the plurality of inlet passages 100a in sequence, and if the plurality of inlet passages 100a are provided in parallel, the refrigerant is distributed to the plurality of inlet passages 100 a. When the outlet passage 100b is plural, the plural outlet passages 100b are arranged in series or in parallel, and if the plural outlet passages 100b are arranged in series, the refrigerant sequentially flows through the plural outlet passages 100b, and if the plural outlet passages 100b are arranged in parallel, the refrigerant is distributed to the plural outlet passages 100 b.
It can be understood that the inlet channel 100a can be reasonably arranged, so that the distribution optimization of the refrigerant of the plurality of tube fin units 100 can be conveniently realized; when the inlet passage 100a is plural, it is advantageous to reduce the flow loss of the refrigerant in the inlet passage 100 a.
For example, in the example of fig. 1, 4, 13, the inlet channel 100a and the outlet channel 100b are respectively one, and the inlet channel 100a communicates with all the heat exchange channels 10 of the plurality of fin units 10, and the outlet channel 100b communicates with all the heat exchange channels 10 of the plurality of fin units 10; for another example, in the example of fig. 7, there are two inlet channels 100a, one of the inlet channels 100a is communicated with all the heat exchange channels 10 of the plurality of fin units 100, the other inlet channel 100a is arranged in series with the above-mentioned one of the inlet channels 100a, one of the outlet channels 100b is provided, and the outlet channel 100b is communicated with all the heat exchange channels 10 of the plurality of fin units 10; for another example, in the example of fig. 8, there are two inlet channels 100a, one of the inlet channels 100a communicating with a portion of the plurality of heat exchange channels 10 of each fin unit 100, the other inlet channel 100a communicating with the other portion of the plurality of heat exchange channels 10 of each fin unit 100, such that the two inlet channels 100a are arranged in parallel, and two outlet channels 100b, one of the outlet channels 100b communicating with a portion of the plurality of heat exchange channels 10 of each fin unit 100, the other outlet channel 100b communicating with the other portion of the plurality of heat exchange channels 10 of each fin unit 100, such that the two outlet channels 100b are arranged in parallel.
It is understood that the number of inlet channels 100a may be equal to or different from the number of outlet channels 100 b.
Optionally, a protrusion is arranged on the body 1 of at least one of the two adjacent single tube fin units 100, and the protrusion stops between the two adjacent single tube fin units 100, so that when the plurality of single tube fin units 100 are sequentially arranged along the thickness direction of the single tube fin unit 100, the interval between the two adjacent single tube fin units 100 is convenient to determine. Wherein, the bulge can be formed by the partial surface of the body 1 protruding towards the direction far away from the thickness central plane of the body 1, and the bulge can be formed into a solid structure or a hollow structure.
For example, a protrusion may be provided on the body 1 of one of the two adjacent single tube fin units 100, and an end surface of a free end of the protrusion may abut against another surface of the two adjacent single tube fin units 100, and at this time, the outer peripheral wall of the heat exchange channel 10 may not abut against the surface of the adjacent single tube fin unit 100, which may protect the heat exchange tube and simplify the structure of the single tube fin unit 100.
It is understood that the shape, number, arrangement mode, arrangement position, etc. of the protrusions can be specifically set according to actual situations. For example, the protrusion between two adjacent fin units 100 may be one or more.
An air conditioner according to an embodiment of the third aspect of the present invention includes the heat exchanger 200 according to the above-described embodiment of the second aspect of the present invention.
According to the air conditioner of the embodiment of the utility model, the cooling or heating performance of the air conditioner can be improved by adopting the heat exchanger 200 of the second aspect of the embodiment.
Other configurations and operations of the air conditioner according to the embodiment of the present invention are known to those skilled in the art and will not be described in detail herein.
In the description of the present invention, it is to be understood that the terms "central," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," "circumferential," and the like are used in the orientations and positional relationships indicated in the drawings for convenience in describing the utility model and to simplify the description, and are not intended to indicate or imply that the referenced device or element must have a particular orientation, be constructed and operated in a particular orientation, and are not to be considered limiting of the utility model. Furthermore, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means two or more unless otherwise specified.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the description herein, references to the description of the term "one embodiment," "some embodiments," "an illustrative embodiment," "an example," "a specific example," or "some examples" or the like mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the utility model. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
While embodiments of the utility model have been shown and described, it will be understood by those of ordinary skill in the art that: various changes, modifications, substitutions and alterations can be made to the embodiments without departing from the principles and spirit of the utility model, the scope of which is defined by the claims and their equivalents.
Claims (11)
1. A tube fin monomer is characterized by comprising a body, wherein an inlet hole and an outlet hole which are communicated along the thickness direction of the body are formed at two ends of the body in the length direction respectively, a plurality of refrigerant inlets are formed on the inner surface of the inlet hole, a plurality of refrigerant outlets are formed on the inner surface of the outlet hole, a plurality of heat exchange channels are defined in the body, the heat exchange channels are arranged at intervals along the width direction of the body, each heat exchange channel extends along the length direction of the body, two ends of each heat exchange channel in the length direction are respectively communicated with the refrigerant inlets and the refrigerant outlets, the cross sectional areas of at least two heat exchange channels in the plurality of heat exchange channels are unequal, and the cross sectional area of the heat exchange channel positioned at the upstream in the at least two heat exchange channels is larger than that of the heat exchange channel positioned at the downstream, the width direction of the body is parallel to the airflow direction.
2. A tube fin unit according to claim 1, wherein the cross-sectional areas of a plurality of said heat exchange channels decrease sequentially in the direction of gas flow.
3. A tube fin cell according to claim 1, wherein the number of heat exchange channels is N, the cross-sectional area of the first N heat exchange channels in the gas flow direction is larger than the cross-sectional area of the remaining heat exchange channels, N, N are positive integers, and 1. ltoreq.N < N,
the cross sectional areas of the first N heat exchange channels are equal; and/or the presence of a gas in the gas,
the cross-sectional areas of the rest of the heat exchange channels are equal.
4. A tube fin unit according to any one of claims 1 to 3, wherein said body is formed in a plate-like structure, and part of the outer peripheral wall of said heat exchange channel projects from the outer surface of said body.
5. A tube fin cell according to claim 4, wherein the plurality of heat exchange channels includes a first heat exchange channel and a second heat exchange channel,
the central axes of the first heat exchange channel and the second heat exchange channel are both positioned on the thickness central plane of the body; alternatively, the first and second electrodes may be,
the central axis of the first heat exchange channel faces one side of the thickness direction of the body and deviates from the thickness central plane of the body, the central axis of the second heat exchange channel faces the other side of the thickness direction of the body and deviates from the thickness central plane of the body, and the first heat exchange channel and the second heat exchange channel are alternately arranged one by one along the width direction.
6. A tube fin unit according to claim 4, wherein the body includes a first plate body and a second plate body, the first plate body and the second plate body each being formed in a plate-like structure, the first plate body and the second plate body being disposed in opposition to collectively define the heat exchange channels.
7. A tube fin unit according to claim 6, wherein the first plate body is formed with a first groove and/or the second plate body is formed with a second groove, each of the heat exchange channels being formed by the first groove and/or the second groove.
8. A tube fin unit according to claim 7, wherein the first plate body is formed with a first groove having a first notch, the second plate body is formed with a second groove having a second notch, the first and second grooves together define the heat exchange channel, and the first and second notches are disposed either directly opposite or offset in the width direction.
9. A heat exchanger, comprising:
a plurality of tube fin units according to any one of claims 1 to 8, wherein the tube fin units are sequentially arranged at intervals along the thickness direction of the tube fin units, so that the inlet holes of the bodies are spliced to form an inlet channel, and the outlet holes of the bodies are spliced to form an outlet channel.
10. The heat exchanger of claim 9, wherein at least one of the inlet channel and/or the outlet channel is plural,
the inlet channels are arranged in series or in parallel, and the outlet channels are arranged in series or in parallel.
11. An air conditioner characterized by comprising the heat exchanger according to claim 9 or 10.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122734731.7U CN216347033U (en) | 2021-11-09 | 2021-11-09 | Pipe fin monomer, heat exchanger and air conditioner |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122734731.7U CN216347033U (en) | 2021-11-09 | 2021-11-09 | Pipe fin monomer, heat exchanger and air conditioner |
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| Publication Number | Publication Date |
|---|---|
| CN216347033U true CN216347033U (en) | 2022-04-19 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202122734731.7U Active CN216347033U (en) | 2021-11-09 | 2021-11-09 | Pipe fin monomer, heat exchanger and air conditioner |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN216347033U (en) |
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2021
- 2021-11-09 CN CN202122734731.7U patent/CN216347033U/en active Active
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